Hydraulic control system for locking pile leg

Abstract

The utility model discloses a hydraulic control system for locking a pile leg. The hydraulic control system comprises an electromagnetic directional valve, a first hydraulic control valve, a second hydraulic control valve, a pressure cylinder, an oil tank and a bolt oil cylinder for locking the pile leg, when the electromagnetic reversing valve is powered on and reverses, the electromagnetic reversing valve is connected with the first hydraulic control valve and the oil supply end, high-pressure oil of the oil supply end is conveyed to the first hydraulic control valve, the first hydraulic control valve is connected with the second hydraulic control valve and the pressure cylinder, and the first hydraulic control valve correspondingly conveys the high-pressure oil to the pressure cylinder and the second hydraulic control valve. The pressure cylinder and the second hydraulic control valve are both connected with the bolt oil cylinder and convey oil to a rod cavity of the bolt oil cylinder for pressurization; a rodless cavity of the bolt oil cylinder is connected with the electromagnetic reversing valve, and the electromagnetic reversing valve is connected with the oil tank and used for enabling high-pressure oil in the rodless cavity of the bolt oil cylinder to flow back to the oil tank so that a pin rod of the bolt oil cylinder can retract and be separated from the pile leg. Therefore, the oil pressure of the rod cavity of the plug pin oil cylinder is improved by at least two times, then the pin is pulled out smoothly and quickly, and the wind power installation efficiency and quality are improved.

Description

Technical Field

[0001] The utility model relates to the technical field of hydraulic control, in particular to a hydraulic control system for locking pile legs. Background Art

[0002] As a key marine engineering equipment, the self-elevating marine engineering platform mainly includes a working platform, pile legs for supporting the working platform, and a locking device for locking the pile legs. That is, after adjusting the relative position of the working platform and the pile legs, the locking device is used to lock the working platform and the pile legs to each other.

[0003] Hydraulic control systems in the prior art, such as Figure 1 As shown, a latch cylinder 50', a hydraulically controlled one-way valve 20', a two-position four-way electromagnetic reversing valve 10' and an oil tank 40' are provided. The two-position four-way electromagnetic reversing valve 10' controls the locking and releasing actions of the latch cylinder 50' on the pile leg 60'.

[0004] Specifically, when the latch cylinder 50' latch locks the pile leg 60', the iron core of the two-position four-way electromagnetic reversing valve 10' is de-energized, and the high-pressure oil at the oil supply end 30' passes through the P port of the two-position four-way electromagnetic reversing valve 10' to the A port, and the A port is connected with the IN port of the hydraulically controlled one-way valve 20', thereby flowing to the OUT port and entering the rodless cavity of the latch cylinder 50', so that the latch of the latch cylinder 50' is extended; the hydraulic oil in the rod cavity of the latch cylinder 50' flows to the B port of the two-position four-way electromagnetic reversing valve 10', and the B port is connected with the T port, and the T port is connected to the oil tank 40', so that the hydraulic oil in the rod cavity returns to the oil tank 40'; thereby achieving the purpose of locking the pile leg 60'.

[0005] When the latch cylinder 50' pulls out the pin to loosen the pile leg 60', the iron core of the two-position four-way solenoid reversing valve 10' is energized, and the two-position four-way solenoid reversing valve 10' performs a reversing action. The high-pressure oil at the oil supply end 30' is passed to the B port through the P port of the two-position four-way solenoid reversing valve 10'. The B port is provided with a three-way connection, which is respectively connected to the X port of the hydraulically controlled one-way valve 20' and the rod chamber of the latch cylinder 50'. The fluid pressure input to the X port of the hydraulically controlled one-way valve 20' opens the hydraulically controlled one-way valve 20', and the hydraulic oil enters the rod chamber of the latch cylinder 50', causing the latch of the latch cylinder 50' to retract; the hydraulic oil in the rodless chamber of the latch cylinder 50' flows to the OUT port of the hydraulically controlled one-way valve 20'. Since the hydraulically controlled one-way valve 20' has been opened, the hydraulic oil flows to the two-position four-way reversing valve DE through the IN port of the hydraulically controlled one-way valve 20'. Port A is connected to port T, which is connected to the oil tank 40', so that the hydraulic oil in the rodless chamber returns to the oil tank 40', thereby achieving the purpose of loosening the pile leg 60'.

[0006] Although the prior art can basically complete the locking work of the bolt cylinder on the pile leg through a single two-position four-way electromagnetic reversing valve, it still has the following defects:

[0007] 1. When installing wind turbines on a working platform of an offshore engineering platform, after the pin of the pin cylinder is inserted into the pile leg, the pin is easily stuck in the socket of the pile leg and difficult to pull out due to the weight and posture change of the working platform. The existing hydraulic control system only has a single two-position four-way electromagnetic reversing valve to control the oil pressure of the pin cylinder. This easily causes the pin cylinder to provide insufficient pressure for the pin pulling action, resulting in the pin being unable to be pulled out normally, thereby affecting the efficiency and quality of wind turbine installation.

[0008] 2. The rescue measures for the pin of the pin cylinder being stuck by the pile leg are currently mainly to manually adjust the system pressure or use a manual hoist to pull out the pin. Manual operation is inefficient, delays the construction period, and poses a safety hazard. Utility Model Content

[0009] In order to overcome the deficiencies of the prior art, the present invention aims to provide a hydraulic control system for locking pile legs.

[0010] The purpose of the utility model is achieved by adopting the following technical solutions: a hydraulic control system for locking pile legs, comprising a solenoid reversing valve, a first hydraulic control valve, a second hydraulic control valve, a booster cylinder, an oil tank and a latch oil cylinder for locking the pile legs;

[0011] When the solenoid reversing valve is energized and reversed, it is connected to the first hydraulic control valve and the oil supply end, and the high-pressure oil at the oil supply end is delivered to the first hydraulic control valve. The first hydraulic control valve is connected to the second hydraulic control valve and the booster cylinder. The first hydraulic control valve delivers the high-pressure oil to the booster cylinder and the second hydraulic control valve respectively. The booster cylinder and the second hydraulic control valve are both connected to the latch cylinder and deliver oil to the rod chamber of the latch cylinder for boosting.

[0012] The rodless chamber of the latch cylinder is connected to an electromagnetic reversing valve, which is connected to the oil tank and is used to flow the high-pressure oil in the rodless chamber of the latch cylinder back to the oil tank, so that the pin rod of the latch cylinder is retracted and separated from the pile leg.

[0013] Furthermore, when the electromagnetic reversing valve is powered off, it is connected to the pin oil cylinder and the oil supply end, and the high-pressure oil in the oil supply end is delivered to the rodless chamber of the pin oil cylinder;

[0014] The rod chamber of the latch cylinder is connected to the second hydraulically controlled valve, the second hydraulically controlled valve is connected to the first hydraulically controlled valve, the first hydraulically controlled valve is connected to the electromagnetic reversing valve, and the electromagnetic reversing valve is connected to the oil tank, so as to flow the high-pressure oil in the rod chamber back to the oil tank through the second hydraulically controlled valve, the first hydraulically controlled valve, and the electromagnetic reversing valve in sequence, so that the pin rod of the latch cylinder is extended and locks the pile leg.

[0015] Furthermore, the solenoid reversing valve is configured as a two-position four-way solenoid reversing valve, wherein the P port of the two-position four-way solenoid reversing valve is connected to the oil supply end, the A port is connected to the rodless chamber of the latch cylinder, the T port is connected to the oil tank, and the B port is connected to the first hydraulic control valve;

[0016] When the two-position four-way electromagnetic reversing valve is powered off, its P port is connected to the A port, and the high-pressure oil at the oil supply end is delivered to the rodless chamber of the latch cylinder; its T port is connected to the B port, and the high-pressure oil of the first hydraulic control valve flows back to the oil tank;

[0017] When the two-position four-way solenoid reversing valve is energized and reversed, its P port is connected with the B port, and the high-pressure oil at the oil supply end is delivered to the first hydraulic control valve; its A port is connected with the T port, and the high-pressure oil in the rodless chamber of the latch cylinder flows back to the oil tank.

[0018] Furthermore, the first hydraulic control valve is configured as a two-position four-way hydraulic control valve, wherein the P1 port of the two-position four-way hydraulic control valve is connected to the B port of the two-position four-way electromagnetic reversing valve, the A1 port is connected to the b port of the boosting cylinder and the second hydraulic control valve, the T1 port is connected to the oil tank, and the B1 port is connected to the a port of the boosting cylinder;

[0019] When the two-position four-way hydraulic control valve is switched, its P1 port is connected with the B1 port, and the high-pressure oil is delivered to the a port of the booster cylinder; the A1 port is connected with the T1 port and the b port of the booster cylinder, and the high-pressure oil at the b port of the booster cylinder flows back to the oil tank through the A1 port and the T1 port;

[0020] When the two-position four-way hydraulic control valve is not reversing, its P1 port is connected to the A1 port, and the high-pressure oil is delivered to the second hydraulic control valve; the B1 port is connected to the T1 port, and the high-pressure oil at the a port of the booster cylinder flows back to the oil tank through the B1 port and the T1 port.

[0021] Furthermore, the second hydraulic control valve is configured as a two-position three-way hydraulic control valve, wherein the P2 port of the two-position three-way hydraulic control valve is connected to the A1 port of the two-position four-way hydraulic control valve and the b port of the booster cylinder, and the A2 port is connected to the c port of the booster cylinder and the rod chamber of the latch cylinder;

[0022] When the two-position three-way hydraulic control valve does not change direction, its P2 port is connected to the A2 port, and the high-pressure oil is delivered to the rod chamber of the latch cylinder;

[0023] When the two-position three-way hydraulic control valve is switched, the high-pressure oil in the rod chamber of the latch cylinder flows back to the oil tank through the A2 port, P2 port, A1 port, P1 port, B port and T port in sequence.

[0024] Furthermore, a hydraulically controlled one-way valve is provided between the two-position four-way solenoid directional valve and the rodless cavity of the latch cylinder, wherein the IN port of the hydraulically controlled one-way valve is connected to the A port of the two-position four-way hydraulically controlled valve, the OUT port is connected to the rodless cavity of the latch cylinder, and the X port is connected to the A2 port of the two-position three-way hydraulically controlled valve and the C port of the booster cylinder;

[0025] When the booster cylinder delivers high-pressure oil to the rod chamber of the latch cylinder through port C and the two-position three-way hydraulic control valve delivers high-pressure oil to port X of the hydraulic control one-way valve at the same time, so that the hydraulic control one-way valve is reversed, and the high-pressure oil in the rodless chamber of the latch cylinder flows back to the oil tank through port OUT, port IN, port A and port T in sequence.

[0026] Furthermore, the oil tank includes a first oil tank and a second oil tank, the first oil tank is connected to the T port of the two-position four-way electromagnetic reversing valve, and the second oil tank is connected to the T1 port of the two-position four-way hydraulic control valve.

[0027] Furthermore, the ratio of the total load area to the pressure action area of ​​the boosting cylinder is (1:2).

[0028] Furthermore, the oil pressure provided by the boost cylinder is twice the system oil pressure.

[0029] Furthermore, a number of latch cylinders are equidistantly arranged around the pile leg, the rodless cavities of several of the latch cylinders are interconnected and oil is synchronously supplied and discharged, and the rod cavities of several of the latch cylinders are interconnected and oil is supplied and discharged synchronously; a number of insertion holes are opened at the positions of the pile leg corresponding to where the latch cylinders are arranged, so that the pin rods of several of the latch cylinders can be synchronously inserted into their respective corresponding insertion holes to lock the pile leg.

[0030] Compared with the prior art, the beneficial effects of the present invention are as follows: the hydraulic control system provided in the embodiment of the present application is provided with a booster cylinder, a first hydraulic control valve and a second hydraulic control valve, the high-pressure oil delivered by the electromagnetic reversing valve is delivered to the booster cylinder through the first hydraulic control valve for boosting treatment, the high-pressure oil pressurized by the booster cylinder is delivered to the rod chamber of the latch cylinder through the second hydraulic control valve, thereby increasing the oil pressure for pulling out the latch cylinder; the high-pressure oil in the rodless chamber of the latch cylinder flows back to the oil tank, achieving the purpose of pulling out the latch cylinder; after the latch cylinder is pulled out, the booster cylinder is reset, and at this time the first hydraulic control valve continues to deliver the high-pressure oil to the second hydraulic control valve, and the second hydraulic control valve delivers high-pressure oil to the rod chamber of the latch cylinder to maintain the pulled-out state of the latch cylinder;

[0031] Compared with the previous implementation method of delivering high-pressure oil to the rod chamber of a single latch cylinder through a single two-position four-way electromagnetic reversing valve, the embodiment of the present application increases the oil pressure of the rod chamber of each latch cylinder by at least 2 times, without the need to manually adjust the system pressure or manually pull out the pin rod of the latch cylinder, thereby reducing work safety risks; and controlling the oil circuit through the hydraulic control valve can reduce electrical control logic, simplify the system, and reduce the failure rate; combined with the function of the hydraulic control valve itself to automatically reverse when it reaches the pressure control point, it is more efficient and has less energy loss than electrical control; thereby, the pin rod of each latch cylinder can be smoothly and quickly pulled out of the pile leg, thereby improving the efficiency and quality of wind power installation. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] Figure 1 Schematic diagram of a hydraulic control system for locking pile legs in the prior art;

[0033] Figure 2 This is a schematic diagram of the hydraulic control system for locking the pile legs in a preferred embodiment of the present utility model.

[0034] In the picture:

[0035] 10', two-position four-way solenoid reversing valve; 20', hydraulically controlled one-way valve; 30', oil supply end; 40', oil tank; 50', latch cylinder; 60', pile leg;

[0036] 10. Two-position four-way solenoid directional control valve; 11. Two-position four-way hydraulic control valve; 12. Two-position three-way hydraulic control valve; 13. Hydraulic control check valve;

[0037] 20. Booster cylinder;

[0038] 30. Oil supply end;

[0039] 40. First fuel tank; 41. Second fuel tank;

[0040] 50. Latch cylinder; 501. Pin rod;

[0041] 60, pile leg; 601, socket. DETAILED DESCRIPTION

[0042] Below, the present invention is further described in conjunction with the accompanying drawings and specific implementation methods. It should be noted that, under the premise of no conflict, the various embodiments or technical features described below can be arbitrarily combined to form new embodiments.

[0043] like Figure 2 As shown, a hydraulic control system for locking a pile leg 60 is used to lock the pile leg 60 between the work platform and the work platform. It can also be used to secure other cylindrical objects. The hydraulic control system for locking the pile leg 60 includes a solenoid reversing valve, a first hydraulically controlled valve, a second hydraulically controlled valve, a booster cylinder 20, a hydraulically controlled check valve 13, an oil tank, and a latch cylinder 50 for locking the pile leg 60.

[0044] The electromagnetic reversing valve is configured as a two-position four-way electromagnetic reversing valve 10 , the first hydraulic control valve is configured as a two-position four-way hydraulic control valve 11 , the second hydraulic control valve is configured as a two-position three-way hydraulic control valve 12 , and the oil tank includes a first oil tank 40 and a second oil tank 41 .

[0045] Several latch cylinders 50 are equidistantly arranged around the leg 60. The rodless chambers of the latch cylinders 50 are interconnected, allowing for simultaneous oil flow in and out of the rodless chambers. The rod chambers of the latch cylinders 50 are also interconnected, allowing for simultaneous oil flow in and out of the rod chambers. This allows for synchronized pressurization control between the latch cylinders 50, as well as synchronized latching and unlatching operations, preventing any latch cylinder from becoming stuck. Sockets 601 are provided at the corresponding locations on the leg 60 where the latch cylinders 50 are located, allowing the pin 501 of each latch cylinder 50 to be inserted into the corresponding socket 601. This secures the leg 60 around its perimeter and improves stability between the leg 60 and the work platform.

[0046] The P port of the two-position four-way solenoid reversing valve 10 is connected to the oil supply end 30 , the A port is connected to the IN port of the hydraulically controlled one-way valve 13 , the T port is connected to the first oil tank 40 , and the B port is connected to the P1 port of the two-position four-way hydraulically controlled valve 11 .

[0047] The OUT port of the hydraulically controlled one-way valve 13 is connected to the rodless chamber of the latch cylinder 50 , and the X port is connected to the A2 port of the two-position three-way hydraulically controlled valve 12 and the C port of the booster cylinder 20 .

[0048] The A1 port of the two-position four-way hydraulic control valve 11 is connected to the b port of the boosting cylinder and the P2 port of the two-position three-way hydraulic control valve 12 , the T1 port is connected to the second oil tank 41 , and the B1 port is connected to the a port of the boosting cylinder.

[0049] The P2 port of the two-position three-way hydraulic control valve 12 is connected to the b port of the boosting cylinder 20 , and the A2 port is connected to the c port of the boosting cylinder and the rod chamber of the latch cylinder 50 .

[0050] The specific working mode of the hydraulic control system of the embodiment of the present application is as follows:

[0051] During the latching process of the latch cylinder 50 , the two-position four-way electromagnetic reversing valve 10 enters a power-off state, the two-position four-way hydraulic control valve 11 does not reverse, and the two-position three-way hydraulic control valve 12 reverses.

[0052] The P port of the two-position, four-way solenoid reversing valve 10 is connected to the oil supply end 30, while the A port is connected to the rodless chambers of the plurality of latch cylinders 50 via a hydraulically controlled one-way valve 13. When the two-position, four-way solenoid reversing valve 10 is de-energized, the P port communicates with the A port, and the B port communicates with the T port. Therefore, the two-position, four-way solenoid reversing valve 10 synchronously delivers high-pressure oil from the oil supply end 30 to the rodless chambers of the plurality of latch cylinders 50 through the P port, A port, IN port, and OUT port, sequentially. This, in turn, causes the rodless chambers of the plurality of latch cylinders 50 to simultaneously generate sufficient oil pressure to extend the pin rod 501 toward the receptacle 601 of the pile leg 60.

[0053] The rod chambers of several latch cylinders 50 are connected to port A2 of the two-position, three-way hydraulic control valve 12. When the oil pressure in the rodless chamber of the latch cylinder 50 is applied, the oil pressure on the left side of the two-position, three-way hydraulic control valve 12 becomes greater than the spring force on the right side, causing the two-position, three-way hydraulic control valve 12 to switch direction, connecting port A2 of the two-position, three-way hydraulic control valve 12 to port P2. Meanwhile, the two-position, four-way hydraulic control valve 11 does not switch direction, so its port P1 is connected to port A1, and its port B1 is connected to port T1.

[0054] Therefore, the high-pressure oil in the rod chambers of several latch cylinders 50 flows back to the first oil tank 40 synchronously through the A2 port, P2 port, A1 port, P1 port, B port and T port in sequence, so that the pin rods 501 of several latch cylinders 50 can be synchronously extended and inserted into the sockets 601 set around the pile legs 60, fixing the four sides of the pile legs 60, and achieving the purpose of locking the pile legs 60 and the work platform. Compared with the previous implementation method of only setting a single latch cylinder 50 to fix one side of the pile leg 60, the locking effect of the pile leg 60 and the work platform is better.

[0055] During the process of pulling out the latch cylinder 50 , the two-position four-way electromagnetic reversing valve 10 enters the energized state and performs a reversing action, the two-position four-way hydraulic control valve 11 is reversed, and the two-position three-way hydraulic control valve 12 is not reversed.

[0056] The P port of the two-position, four-way solenoid reversing valve 10 is connected to the oil supply port 30. When the two-position, four-way solenoid reversing valve 10 is energized, the P port communicates with the B port, and the A port communicates with the T port. Therefore, the two-position, four-way solenoid reversing valve 10 delivers high-pressure oil from the oil supply port 30 to the P1 port of the two-position, four-way hydraulic control valve 11 through the P and B ports.

[0057] If the pin 501 of the latch cylinder 50 becomes stuck, the oil pressure rises to the control point of the two-position, four-way hydraulic control valve 11. The oil pressure on the left side of the two-position, four-way hydraulic control valve 11 becomes greater than the elastic force of the spring on the right side, causing the two-position, four-way hydraulic control valve 11 to reverse direction, achieving the purpose of automatically identifying the stuck pin without human intervention or stopping the machine. The automatic reversal of the two-position, four-way hydraulic control valve 11 connects its P1 port to B1, and its A1 port to T1. Meanwhile, the two-position, three-way hydraulic control valve 12 does not reverse direction, so its P2 port is connected to A2 port.

[0058] Therefore, the two-position, four-way solenoid directional valve 10 sequentially delivers high-pressure oil from the oil supply port 30 through ports P, B, P1, and B1 to port a of the booster cylinder 20, where it then enters the rodless chamber of the booster cylinder 20. The high-pressure oil in the intermediate chamber of the booster cylinder 20 then flows back to the second oil tank 41 through ports b, A1, and T1. The high-pressure oil in the rod chamber of the booster cylinder 20 is synchronously delivered through port c to the rod chamber of each latch cylinder 50 and port X of the hydraulically controlled check valve 13. This instantly increases the oil pressure in the rod chamber of each latch cylinder 50, ensuring that each latch cylinder 50 has the pressure to retract the pin 501. This process also consumes less energy than an electrical control method.

[0059] By supplying high-pressure oil to port X of the hydraulically controlled check valve 13, which serves as an external control port or remote control port for inputting control pressure, reverse flow control of the hydraulically controlled check valve 13 is achieved. Therefore, the high-pressure oil in the rodless chamber of each latch cylinder 50 flows back to the first oil tank 40 through the OUT port, IN port, A port, and T port in sequence, allowing the pin rod 501 of each latch cylinder 50 to synchronously retract and disengage from the socket 601 of the leg 60, thereby unlocking the leg 60 from the work platform.

[0060] In addition, after the pin rod 501 of the latch cylinder 50 completes the pin pulling action, the two-position four-way solenoid reversing valve 10 remains energized and performs a reversing action, the oil pressure of the booster cylinder 20 drops, the booster cylinder 20 enters a reset action, and the two-position four-way hydraulic control valve 11 and the two-position three-way hydraulic control valve 12 do not reverse.

[0061] Therefore, the two-position four-way electromagnetic reversing valve 10 delivers the high-pressure oil at the oil supply end 30 to the P1 port of the two-position four-way hydraulic control valve 11 through the P port and the B port.

[0062] Since the pin removal has been completed, the oil pressure will not rise to the control point of the two-position four-way hydraulic control valve 11. Therefore, the two-position four-way hydraulic control valve 11 will not switch direction. The P1 port of the two-position four-way hydraulic control valve 11 is connected to the A1 port, and the B1 port is connected to the T1 port. In addition, the two-position three-way hydraulic control valve 12 does not switch direction either, so its P2 port is connected to the A2 port.

[0063] Therefore, the two-position, four-way solenoid directional valve 10 delivers high-pressure oil from the oil supply port 30 sequentially through ports P, B, P1, A1, P2, and A2 to the rod chamber of each latch cylinder 50. Simultaneously, high-pressure oil from the two-position, three-way solenoid directional valve is delivered through port A2 to port X of the hydraulically-controlled check valve 13, maintaining reverse flow control of the hydraulically-controlled check valve 13. This allows the high-pressure oil in the rodless chamber of each latch cylinder 50 to flow back to the first oil tank 40 sequentially through ports OUT, IN, A, and T. This maintains the retracted state of the pin 501 of each latch cylinder 50.

[0064] Preferably, the ratio of the total load area to the pressure-applied area of ​​the booster cylinder 20 provided in the embodiment of the present application is (1:2). The system oil pressure is 16 MPa. Based on the ratio of the total load area to the pressure-applied area of ​​the booster cylinder 20, it can be seen that the oil pressure provided by the booster cylinder 20 is twice the system oil pressure. Therefore, the embodiment of the present application can increase the oil pressure of the latch cylinder 50 to at least 32 MPa by providing the booster cylinder 20 for pulling the pin.

[0065] In this way, the hydraulic control system provided in the embodiment of the present application delivers the high-pressure oil delivered by the electromagnetic reversing valve to the booster cylinder 20 through the two-position four-way hydraulic control valve 11 for boosting treatment, and the high-pressure oil boosted by the booster cylinder 20 is synchronously delivered to the rod chamber of each latch cylinder 50 through the two-position three-way hydraulic control valve 12, thereby increasing the oil pressure of the latch cylinder 50 for pulling out the pin.

[0066] Compared with the previous implementation method of delivering high-pressure oil to the rod chamber of a single latch cylinder 50 through a single two-position four-way electromagnetic reversing valve 10, the embodiment of the present application increases the oil pressure of the rod chamber of each latch cylinder 50 by at least 2 times, and there is no need to manually adjust the system pressure or manually pull out the pin rod 501 of the latch cylinder 50, thereby reducing work safety risks; and controlling the oil circuit by the hydraulic control valve can reduce electrical control logic, simplify the system, and reduce the failure rate; combined with the function of the hydraulic control valve itself to automatically reverse when reaching the pressure control point, it is more efficient and has less energy loss than electrical control; thereby, the pin rod 501 of each latch cylinder 50 can be smoothly and quickly pulled out of the pile leg 60, thereby improving the efficiency and quality of wind power installation.

[0067] The above-mentioned embodiments are only preferred embodiments of the present invention and cannot be used to limit the scope of protection of the present invention. Any non-substantial changes and replacements made by technicians in this field on the basis of the present invention fall within the scope of protection required by the present invention.

Claims

1. A hydraulic control system for locking pile legs, characterized in that: It includes a solenoid reversing valve, a first hydraulic control valve, a second hydraulic control valve, a booster cylinder, an oil tank and a latch oil cylinder for locking the pile legs; When the solenoid reversing valve is energized and reversed, it is connected to the first hydraulic control valve and the oil supply end, and the high-pressure oil at the oil supply end is delivered to the first hydraulic control valve. The first hydraulic control valve is connected to the second hydraulic control valve and the booster cylinder. The first hydraulic control valve delivers the high-pressure oil to the booster cylinder and the second hydraulic control valve respectively. The booster cylinder and the second hydraulic control valve are both connected to the latch cylinder and deliver oil to the rod chamber of the latch cylinder for boosting. The rodless chamber of the latch cylinder is connected to an electromagnetic reversing valve, which is connected to the oil tank and is used to flow the high-pressure oil in the rodless chamber of the latch cylinder back to the oil tank, so that the pin rod of the latch cylinder is retracted and separated from the pile leg.

2. The hydraulic control system for locking pile legs according to claim 1, characterized in that: When the electromagnetic reversing valve is powered off, it is connected to the pin oil cylinder and the oil supply end, and the high-pressure oil in the oil supply end is delivered to the rodless chamber of the pin oil cylinder; The rod chamber of the latch cylinder is connected to the second hydraulically controlled valve, the second hydraulically controlled valve is connected to the first hydraulically controlled valve, the first hydraulically controlled valve is connected to the electromagnetic reversing valve, and the electromagnetic reversing valve is connected to the oil tank, so as to flow the high-pressure oil in the rod chamber back to the oil tank through the second hydraulically controlled valve, the first hydraulically controlled valve, and the electromagnetic reversing valve in sequence, so that the pin rod of the latch cylinder is extended and locks the pile leg.

3. The hydraulic control system for locking pile legs according to claim 2, characterized in that: The solenoid reversing valve is configured as a two-position four-way solenoid reversing valve, wherein the P port of the two-position four-way solenoid reversing valve is connected to the oil supply end, the A port is connected to the rodless chamber of the latch cylinder, the T port is connected to the oil tank, and the B port is connected to the first hydraulic control valve; When the two-position four-way electromagnetic reversing valve is powered off, its P port is connected to the A port, and the high-pressure oil at the oil supply end is delivered to the rodless chamber of the latch cylinder; its T port is connected to the B port, and the high-pressure oil of the first hydraulic control valve flows back to the oil tank; When the two-position four-way solenoid reversing valve is energized and reversed, its P port is connected with the B port, and the high-pressure oil at the oil supply end is delivered to the first hydraulic control valve; its A port is connected with the T port, and the high-pressure oil in the rodless chamber of the latch cylinder flows back to the oil tank.

4. The hydraulic control system for locking pile legs according to claim 3, characterized in that: The first hydraulic control valve is configured as a two-position four-way hydraulic control valve, wherein the P1 port of the two-position four-way hydraulic control valve is connected to the B port of the two-position four-way electromagnetic reversing valve, the A1 port is connected to the b port of the boosting cylinder and the second hydraulic control valve, the T1 port is connected to the oil tank, and the B1 port is connected to the a port of the boosting cylinder; When the two-position four-way hydraulic control valve is switched, its P1 port is connected with the B1 port, and the high-pressure oil is delivered to the a port of the booster cylinder; the A1 port is connected with the T1 port and the b port of the booster cylinder, and the high-pressure oil at the b port of the booster cylinder flows back to the oil tank through the A1 port and the T1 port; When the two-position four-way hydraulic control valve is not reversing, its P1 port is connected to the A1 port, and the high-pressure oil is delivered to the second hydraulic control valve; the B1 port is connected to the T1 port, and the high-pressure oil at the a port of the booster cylinder flows back to the oil tank through the B1 port and the T1 port.

5. The hydraulic control system for locking pile legs according to claim 4, characterized in that: The second hydraulic control valve is configured as a two-position three-way hydraulic control valve, wherein the P2 port of the two-position three-way hydraulic control valve is connected to the A1 port of the two-position four-way hydraulic control valve and the b port of the booster cylinder, and the A2 port is connected to the c port of the booster cylinder and the rod chamber of the latch cylinder; When the two-position three-way hydraulic control valve does not change direction, its P2 port is connected to the A2 port, and the high-pressure oil is delivered to the rod chamber of the latch cylinder; When the two-position three-way hydraulic control valve is switched, the high-pressure oil in the rod chamber of the latch cylinder flows back to the oil tank through the A2 port, P2 port, A1 port, P1 port, B port and T port in sequence.

6. The hydraulic control system for locking pile legs according to claim 5, characterized in that: A hydraulically controlled one-way valve is provided between the two-position four-way solenoid directional control valve and the rodless cavity of the latch cylinder, wherein the IN port of the hydraulically controlled one-way valve is connected to the A port of the two-position four-way hydraulically controlled valve, the OUT port is connected to the rodless cavity of the latch cylinder, and the X port is connected to the A2 port of the two-position three-way hydraulically controlled valve and the C port of the booster cylinder; When the booster cylinder delivers high-pressure oil to the rod chamber of the latch cylinder through port C and the two-position three-way hydraulic control valve delivers high-pressure oil to port X of the hydraulic control one-way valve at the same time, so that the hydraulic control one-way valve is reversed, and the high-pressure oil in the rodless chamber of the latch cylinder flows back to the oil tank through port OUT, port IN, port A and port T in sequence.

7. The hydraulic control system for locking pile legs according to claim 6, characterized in that: The oil tank includes a first oil tank and a second oil tank, wherein the first oil tank is connected to the T port of the two-position four-way electromagnetic reversing valve, and the second oil tank is connected to the T1 port of the two-position four-way hydraulic control valve.

8. The hydraulic control system for locking pile legs according to any one of claims 1 to 7, characterized in that: The ratio of the total load area of ​​the boosting cylinder to the pressure action area is (1:2).

9. The hydraulic control system for locking pile legs according to claim 8, characterized in that: The oil pressure provided by the booster cylinder is twice the system oil pressure.

10. The hydraulic control system for locking pile legs according to any one of claims 1 to 7, characterized in that: A number of latch cylinders are equidistantly arranged around the pile leg, the rodless cavities of several of the latch cylinders are interconnected and oil is synchronously supplied and discharged, and the rod cavities of several of the latch cylinders are interconnected and oil is synchronously supplied and discharged; a number of insertion holes are provided at positions of the pile leg corresponding to the positions where the latch cylinders are arranged, so that the pin rod of each of the latch cylinders can be synchronously inserted into the corresponding insertion holes to lock the pile leg.

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